Fluid parameter measurement for industrial sensing applications using acoustic pressures

ABSTRACT

In industrial sensing applications at least one parameter of at least one fluid in a pipe  12  is measured using a spatial array of acoustic pressure sensors  14,16,18  placed at predetermined axial locations x 1 , x 2 , x 3  along the pipe  12 . The pressure sensors  14,16,18  provide acoustic pressure signals P 1 (t), P 2 (t), P 3 (t) on lines  20,22,24  which are provided to signal processing logic  60  which determines the speed of sound a mix  of the fluid (or mixture) in the pipe  12  using acoustic spatial array signal processing techniques with the direction of propagation of the acoustic signals along the longitudinal axis of the pipe  12 . Numerous spatial array-processing techniques may be employed to determine the speed of sound a mix . The speed of sound a mix  is provided to logic  48 , which calculates the percent composition of the mixture, e.g., water fraction, or any other parameter of the mixture, or fluid, which is related to the sound speed a mix . The logic  60  may also determine the Mach number Mx of the fluid. The acoustic pressure signals P 1 (t), P 2 (t), P 3 (t) measured are lower frequency (and longer wavelength) signals than those used for ultrasonic flow meters, and thus is more tolerant to inhomogeneities in the flow. No external source is required and thus may operate using passive listening. The invention will work with arbitrary sensor spacing and with as few as two sensors if certain information is known about the acoustic properties of the system. The sensor may also be combined with an instrument, an opto-electronic converter and a controller in an industrial process control system.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is an continuation-in-part of commonly owned co-pending U.S. patent application, Ser. No., 09/344,094, entitled “Fluid Parameter Measurement in Pipes Using Acoustic Pressures”, filed Jun. 25, 1999, now U.S. Pat. No. 6,354,147, which is a continuation-in part of Ser. No., 09/105,534, entitled “Fluid Parameter Measurement in Pipes Using Acoustic Pressures”, filed Jun. 26, 1998, now abandoned and contains subject matter related to that disclosed in commonly owned co-pending U.S. patent applications: Ser. No. 09/344,070, entitled “Measurement of Propagating Acoustic Waves in Compliant Pipes”, filed Jun. 25, 1999, Ser. No. 09/344,069, now U.S. Pat. No. 6,435,030, entitled “Displacement Based Pressure Sensor Measuring Unsteady Pressure in a Pipe”, filed Jun. 25, 1999 and Ser. No. 09/344,093, entitled “Non-Intrusive Fiber Optic Pressure Sensor for Measuring Unsteady Pressures within a Pipe”, filed Jun. 25, 1999, now U.S. Pat. No. 6,450,037, all of which are incorporated herein by reference.

TECHNICAL FIELD

This invention relates to fluid parameter measurement in pipes and more particularly to measuring speed of sound and parameters related thereto of fluids in pipes using acoustic pressures for use in industrial sensing applications.

BACKGROUND ART

An industrial process sensor is typically a transducer that responds to a measurand with a sensing element and converts the variable to a standardized transmission signal, e.g., an electrical or optical signal, that is a function of the measurand. Industrial process sensors utilize transducers that include flow measurements of an industrial process such as that derived from slurries, liquids, vapors and gasses in refinery, chemical, paper, pulp, petroleum, gas, pharmaceutical, food, mining, minerals and other fluid processing plants. Industrial process sensors are often placed in or near the process fluids, or in field applications. Often, these field applications are subject to harsh and varying environmental conditions that provide challenges for designers of such sensors. Flow measurement is one of the largest segments of the industrial sensing and instrumentation market. Industries in which flow measurement is prevalent includes petroleum, chemical, pulp, paper, food, and mining and minerals.

Typical electronic, or other, transducers of the prior art often cannot be placed in industrial process environments due to sensitivity to electromagnetic interference, radiation, heat, corrosion, fire, explosion, or other environmental factors. It is for these reasons that fiber optic based sensors are being incorporated into industrial process control environments in increasing number.

Further, it is known that the speed of sound a_(mix) of fluids in pipes may be used to determine various parameters of the fluid, such as is described in U.S. Pat. No. 4,080,837, entitled “Sonic Measurement of Flow Rate and Water Content of Oil-Water Streams”, to Alexander et al., U.S. Pat. No. 5,115,670, entitled “Measurement of Fluid Properties of Two-Phase Fluids Using an Ultrasonic Meter”, to Shen, and U.S. Pat. No. 4,114,439, entitled “Apparatus for Ultrasonically Measuring Physical Parameters of Flowing Media”, to Fick. Such techniques have a pair of acoustic transmitters/receivers (transceivers) that generate a sound signal and measure the time it takes for the sound signal to travel between the transceivers. This is also known as a “sing-around” or “transit time” method. However, such techniques require precise control of the acoustic source and are costly and/or complex to implement in electronics.

Also, these techniques use ultrasonic acoustic signals as the sound signal measured, which are high frequency, short wavelength signals (i.e., wavelengths that are short compared to the diameter of the pipe). Typical ultrasonic devices operate near 200 k Hz, which corresponds to a wavelength of about 0.3 inches in water. In general, to allow for signal propagation through the fluid in an unimpeded and thus interpretable manner, the fluid should be homogeneous down to length scales of several times smaller than the acoustic signal wavelength. Thus, the criteria for homogeneity of the fluid becomes increasingly stricter with shorter wavelength signals. Consequently, inhomogeneities in the fluid, such as bubbles, gas, dirt, sand, slugs, stratification, globules of liquid, and the like, will reflect or scatter the transmitted ultrasonic signal. Such reflection and scattering inhibit the ability of the instrument to determine the propagation velocity. For this reason, the application of ultrasonic flowmeters have been limited primarily to well-mixed flows.

SUMMARY OF THE INVENTION

Objects of the present invention include provision of a system for measuring the speed of sound of fluids in pipes in industrial fluid processes.

According to the present invention, an apparatus for industrial sensing applications for measuring at least one parameter of a mixture of at least one fluid in a pipe, comprising a spatial array of at least two pressure sensors, disposed at different axial locations along the pipe, and each measuring an acoustic pressure within the pipe at a corresponding axial location, each of said sensors providing an acoustic pressure signal indicative of the acoustic pressure within the pipe at said axial location of a corresponding one of said sensors; and a signal processor, responsive to said pressure signals, which provides a signal indicative of a speed of sound of the mixture in the pipe.

According further to the present invention, the signal processor comprises logic that calculates a speed at which sound propagates along the spatial array.

According further to the present invention, the signal processor comprises logic that calculates a frequency domain representation of (or frequency based signal for) each of the acoustic pressures signals. According still further to the present invention, the signal processor comprises logic that calculates a ratio of two of the frequency signals. In still further accord to the present invention, the sensors comprise at least three sensors.

According still further to the present invention, the pressure sensors are fiber optic Bragg grating-based pressure sensors. Still further accord to the present invention, at least one of the pressure sensors measures a circumferential-averaged pressure at a given axial location of the sensor. Further according to the present invention, at least one of the pressure sensors measures pressure at more than one point around a circumference of the pipe at a given axial location of the sensor.

The present invention provides a significant improvement over the prior art by providing a measurement of the speed of sound a_(mix) of a mixture of one or more fluids within a pipe (where a fluid is defined as a liquid or a gas) by using an axial array of acoustic (or ac, dynamic, unsteady, or time varying) pressure measurements along the pipe. An explicit acoustic noise source is not required, as the background acoustic noises within the pipe (or fluid therein) will likely provide sufficient excitation to enable characterization of the speed of sound of the mixture by merely passive acoustic listening.

The invention works with acoustic signals having lower frequencies (and thus longer wavelengths) than those used for ultrasonic meters, such as below about 20 k Hz (depending on pipe diameter). As such, the invention is more tolerant to the introduction of gas, sand, slugs, or other inhomogeneities in the flow.

The invention will work with arbitrary sensor spacing and arbitrary flow Mach numbers Mx; however, if the sensors are equally spaced and the axial velocity of the flow is small and therefore negligible compared to the speed of sound in the mixture (i.e., Mach number of the mixture Mx is small compared to one), the speed of sound a_(mix) may be determined as an explicit function of the frequency domain representation (frequency based signal) for the acoustic pressure signals at a given evaluation frequency ω.

Since the speed of sound is an intrinsic property of mixtures, the present invention can be used to measure any parameter (or characteristic) of any mixture of one or more fluids in a pipe in which such parameter is related to the speed of sound of the mixture a_(mix), e.g., fluid fraction, temperature, salinity, sand particles, slugs, pipe properties, etc. or any other parameter of the mixture that is related to the speed of sound of the mixture. For example, the present invention may be used to measure fluid volume fractions (or composition or cut or content) of a mixture of any number of fluids in which the speed of sound of the mixture a_(mix) is related to (or is substantially determined by), the volume fractions of two constituents of the mixture, e.g., oil/water, oil/gas, water/gas. Also, the present invention can be used to measure the speed of sound of any mixture and can then be used in combination with other known quantities to derive phase content of mixtures with multiple (more than two) constituents.

The present invention allows the speed of sound to be determined in a pipe independent of pipe orientation, i.e., vertical, horizontal, or any orientation therebetween. Also, the invention does not require any disruption to the flow within the pipe (e.g., an orifice or venturi). Further, the invention uses ac (or unsteady or dynamic) pressure measurements as opposed to static (dc) pressure measurements and is therefore less sensitive to static shifts (or errors) in sensing. Furthermore, if harsh environment fiber optic pressure sensors are used to obtain the pressure measurements, such sensors eliminate the need for any electronic components down-hole, thereby improving reliability of the measurement.

Also, a strain gauge (optical, electrical, etc.) that measures hoop strain on the pipe may be used to measure the ac pressure. Fiber optic wrapped sensors may be used as optical strain gauges to provide circumferentially averaged pressure. Thus, the present invention provides non-intrusive measurements of the speed of sound (and other corresponding parameters), which enables real time monitoring and optimization for oil and gas exploration and production, or for other applications.

Also, the invention may be combined with a controller and other devices and used in an industrial process control system.

The foregoing and other objects, features, and advantages of the present invention will become more apparent in light of the following detailed description of exemplary embodiments thereof.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic block diagram of a fluid parameter measurement system, in accordance with the present invention.

FIG. 2 is a graph of the speed of sound of a mixture versus the percent water volume fraction for an oil/water mixture, in accordance with the present invention.

FIG. 3 is a transmission matrix model for the acoustics of an example pipe having 9 sections and a radiation impedance ζ_(rad), in accordance with the present invention.

FIG. 4, illustrations (a)-(c), are graphs of axial values for ρ_(mix), a_(mix), h_(water) properties of a mixture for the segments of the pipe of FIG. 3, in accordance with the present invention.

FIG. 5 is a graph of magnitude and phase versus frequency for a ratio of two pressures P1/P2, for radiation impedance of 1.0, water fraction of 50%, and axial properties of FIG. 4, in accordance with the present invention.

FIG. 6 is a graph of magnitude and phase versus frequency for a ratio of two pressures P1/P3, for radiation impedance of 1.0, water fraction of 50%, and axial properties of FIG. 4, in accordance with the present invention.

FIG. 7 is a graph of the magnitude of the speed of sound estimate versus an error term over a range of frequencies, using the frequency responses of FIGS. 5,6, in accordance with the present invention.

FIG. 8 is a graph of magnitude and phase versus frequency for a ratio of two pressures P1/P2, for radiation impedance of 0.5, water fraction of 50%, and constant axial properties of the mixture, in accordance with the present invention.

FIG. 9 is a graph of magnitude and phase versus frequency for a ratio of two pressures P1/P3, for radiation impedance of 0.5, water fraction of 50%, and constant axial properties of the mixture, in accordance with the present invention.

FIG. 10 is a graph of magnitude and phase versus frequency for a ratio of two pressures P1/P2, for radiation impedance of 0.5, water fraction of 5%, and constant axial properties of the mixture, in accordance with the present invention.

FIG. 11 is a graph of magnitude and phase versus frequency for a ratio of two pressures P1/P3, for radiation impedance of 0.5, water fraction of 5%, and constant axial properties of the mixture, in accordance with the present invention.

FIG. 12 is a graph of the magnitude of the speed of sound estimate versus an error term over a range of frequencies, using the frequency response for two different percent water fractions, of FIGS. 8-11, in accordance with the present invention.

FIG. 13 is a contour plot of speed of sound versus axial Mach versus an error term, for 5% water fraction, Mach number of 0.05, at 25 Hz, in accordance with the present invention.

FIG. 14 is a contour plot of speed of sound versus axial Mach versus an error term, for 50% water fraction, Mach number of 0.05, at 25 Hz, in accordance with the present invention.

FIG. 15 is a portion of a logic flow diagram for logic of FIG. 1, in accordance with the present invention.

FIG. 16 is a continuation of the logic flow diagram of FIG. 15, in accordance with the present invention.

FIG. 17 is a schematic block diagram of a fluid parameter measurement system, in an industrial process control system, using fiber optic sensors, in accordance with the present invention.

FIG. 18 is a plot of speed of sound against wall thickness of a pipe for a rigid and a non-rigid pipe, in accordance with the present invention.

FIG. 19 is a cross-sectional view of a pipe, showing a plurality of sensors around the circumference of the pipe, in accordance with the present invention.

FIG. 20 is a side view of a pipe having an isolating sleeve around the sensing region of the pipe, in accordance with the present invention.

FIG. 21 is an end view of a pipe showing pressure inside and outside the pipe, in accordance with the present invention.

FIG. 22 is a side view of a pipe having optical fiber wrapped around the pipe at each unsteady pressure measurement location and a pair of Bragg gratings around each optical wrap, in accordance with the present invention.

FIG. 23 is a side view of a pipe having optical fiber wrapped around the pipe at each unsteady pressure measurement location with a single Bragg grating between each pair of optical wraps, in accordance with the present invention.

FIG. 24 is a side view of a pipe having optical fiber wrapped around the pipe at each unsteady pressure measurement location without Bragg gratings around each of the wraps, in accordance with the present invention.

FIG. 25 is an alternative geometry of an optical wrap of FIGS. 21,22, of a radiator tube geometry, in accordance with the present invention.

FIG. 26 is an alternative geometry of an optical wrap of FIGS. 21,22, of a race track geometry, in accordance with the present invention.

FIG. 27 is a side view of a pipe having a pair of gratings at each axial sensing location, in accordance with the present invention.

FIG. 28 is a side view of a pipe having a single grating at each axial sensing location, in accordance with the present invention.

FIG. 29 is a top view of three alternative strain gauges, in accordance with the present invention.

FIG. 30 is a side view of a pipe having three axially spaced strain gauges attached thereto, in accordance with the present invention.

FIG. 31 is an end view of a pipe having three unsteady pressure sensors spaced apart from each other within the pipe, in accordance with the present invention.

FIG. 32 is a side view of a pipe having three unsteady pressure sensors spaced axially within the pipe, in accordance with the present invention.

FIG. 33 is a side view of a pipe having three unsteady pressure sensors axially and radially spaced within the pipe, in accordance with the present invention.

FIG. 34 is a side view of a pipe having an inner tube with axially distributed optical fiber wraps for unsteady pressure sensors, in accordance with the present invention.

FIG. 35 is a side view of a pipe having an inner tube with axially distributed unsteady pressure sensors located along the tube, in accordance with the present invention.

FIG. 36 is a side view of a pipe having an inner tube with three axially distributed hydrophones located within the tube, in accordance with the present invention.

FIG. 37 is a diagram showing the propagation of acoustic waves from a single source in two dimensional space onto a spatial array, in accordance with the present invention.

FIG. 38 is a side view of a pipe having left and right travelling acoustic waves propagating along the pipe, in accordance with the present invention.

FIG. 39 is a diagram showing the propagation of acoustic waves from two sources in two dimensional space onto a spatial array, in accordance with the present invention.

FIG. 40 is a schematic block diagram of an alternative embodiment of a fluid parameter measurement system, in accordance with the present invention.

FIG. 41 is a graph of speed of sound versus water cut, in accordance with the present invention.

BEST MODE FOR CARRYING OUT THE INVENTION

Referring to FIG. 1, a pipe (or conduit) 12 has three acoustic pressure sensors 14,16,18, located at three locations x₁,x₂,x₃ along the pipe 12. The pressure may be measured through holes in the pipe 12 ported to external pressure sensors or by other techniques discussed hereinafter. The pressure sensors 14,16,18 provide pressure time-varying signals P₁(t),P₂(t),P₃(t) on lines 20,22,24, to known Fast Fourier Transform (FFT) logics 26,28,30, respectively. The FFT logics 26,28,30 calculate the Fourier transform of the time-based input signals P₁(t),P₂(t),P₃(t) and provide complex frequency domain (or frequency based) signals P₁(ω),P₂(ω),P₃(ω) on lines 32,34,36 indicative of the frequency content of the input signals. Instead of FFT's, any other technique for obtaining the frequency domain characteristics of the signals P₁(t),P₂(t),P₃(t), may be used. For example, the cross-spectral density and the power spectral density may be used to form a frequency domain transfer functions (or frequency response or ratios) discussed hereinafter.

Also, some or all of the functions within the logic 60 may be implemented in software (using a microprocessor or computer) and/or firmware, or may be implemented using analog and/or digital hardware, having sufficient memory, interfaces, and capacity to perform the functions described herein.

Acoustic pressure sensors 14,16,18 sense acoustic pressure signals that, as measured, are lower frequency (and longer wavelength) signals than those used for ultrasonic flow meters of the prior art, and thus the current invention is more tolerant to inhomogeneities in the flow. In addition, the present invention differs from prior art fluid parameter measurement devices in that the present invention incorporates the compliance of the pipe to determine the effective speed of sound of the pipe/fluid system. The typical frequency range for acoustic pressure signals of the present invention is from about 10 Hz to about 10,000 Hz. The acoustic pressure signals are generated within the fluid of the pipe 12 by a variety of non-discrete sources such as remote machinery, pumps, valves, elbows, as well as the fluid flow itself. It is this last source, the fluid flowing within the pipe, that is a generic source of acoustic noise that assures a minimum level of acoustics for any fluid piping systems for which the present invention takes unique advantage. The flow generated acoustics increase with mean flow velocity and the overall noise levels (acoustic pressure levels) are a function of the generating mechanism and the damping mechanism. Experience indicates that pipe systems typically have sufficient ambient noise levels of 100 to 180 dbA. As such, no external discrete noise source is required within the present invention and thus may operate using passive listening. It is within the scope of the present that the pressure sensor spacing may be known or arbitrary and that as few as two sensors are required if certain information is known about the acoustic properties of the system as will be more fully described herein below.

The frequency signals P₁(ω),P₂(ω),P₃(ω) are fed to a_(mix)-Mx Calculation Logic 40 which provides a signal on a line 46 indicative of the speed of sound of the mixture a_(mix) (discussed more hereinafter). The a_(mix) signal is provided to map (or equation) logic 48, which converts a_(mix) to a percent composition of the fluid and provides a % Comp signal on a line 50 indicative thereof (as discussed hereinafter). Also, if the Mach number Mx is not negligible and is desired to be known, the calculation logic 40 may also provide a signal Mx on a line 59 indicative of the Mach number Mx (as discussed hereinafter).

More specifically, for planar one-dimensional acoustic waves in a homogenous mixture, it is known that the acoustic pressure field P(x,t) at a location x along a pipe, where the wavelength λ of the acoustic waves to be measured is long compared to the diameter d of the pipe 12 (i.e., λ/d>>1), may be expressed as a superposition of a right traveling wave and a left traveling wave, as follows:

P(x,t)=(Ae ^(−ik) ^(_(r)) ^(x) +Be ^(+ik) ^(_(l)) ^(x))e ^(iωt)  Eq. 1

where A,B are the frequency-based complex amplitudes of the right and left traveling waves, respectively, x is the pressure measurement location along a pipe, ω is frequency (in rad/sec, where ω=2πf), and k_(r),k_(l) are wave numbers for the right and left travelling waves, respectively, which are defined as: $\begin{matrix} {k_{r} \equiv {\left( \frac{\omega}{a_{m\quad i\quad x}} \right)\frac{1}{1 + M_{x}}\quad {and}\quad k_{l}} \equiv {\left( \frac{\omega}{a_{m\quad i\quad x}} \right)\frac{1}{1 - M_{x}}}} & {{Eq}.\quad 2} \end{matrix}$

where a_(mix) is the speed of sound of the mixture in the pipe, ω is frequency (in rad/sec), and M_(x) is the axial Mach number of the flow of the mixture within the pipe, where: $\begin{matrix} {M_{x} \equiv {\frac{V_{m\quad i\quad x}}{a_{m\quad i\quad x}}\quad {where}\quad {Vmix}\quad {is}\quad {the}\quad {axial}}} & {{Eq}.\quad 3} \end{matrix}$

velocity of the mixture. For non-homogenous mixtures, the axial Mach number represents the average velocity of the mixture and the low frequency acoustic field description remains substantially unaltered.

The frequency domain representation P(x,ω) of the time-based acoustic pressure field P(x,t) within a pipe, is the coefficient of the e^(iωt) term of Eq. 1, as follows:

P(x,ω)=Ae ^(−ik) ^(_(r)) ^(x) +Be ^(+ik) ^(_(l)) ^(x)  Eq. 4

Referring to FIG. 1, we have found that using Eq. 4 for P(x,ω) at three axially distributed pressure measurement locations x₁,x₂,x₃ along the pipe 12 leads to an equation for a_(mix) as a function of the ratio of frequency based pressure measurements, which allows the coefficients A,B to be eliminated. For optimal results, A and B are substantially constant over the measurement time and substantially no sound (or acoustic energy) is created or destroyed in the measurement section. The acoustic excitation enters the test section only through the ends of the test section 51 and, thus, the speed of sound within the test section 51 can be measured independent of the acoustic environment outside of the test section. In particular, the frequency domain pressure measurements P₁(ω),P₂(ω),P₃(ω) at the three locations x₁,x₂,x₃, respectively, along the pipe 12 using Eq. 1 for right and left traveling waves are as follows:

P ₁(ω)=P(x=x ₁,ω)=Ae ^(−ik) ^(_(r)) ^(x) ^(₁) +Be ^(+ik) ^(_(l)) ^(x) ^(₁)   Eq. 5

P ₂(ω)=P(x=x ₂,ω)=Ae ^(−ik) ^(_(r)) ^(x) ^(₂) +Be ^(+ik) ^(_(l)) ^(x) ^(₂)   Eq. 6

P ₃(ω)=P(x=x ₃,ω)=Ae ^(−ik) ^(_(r)) ^(x) ^(₃) +Be ^(+ik) ^(_(l)) ^(x) ^(₃)   Eq. 7

where, for a given frequency, A and B are arbitrary constants describing the acoustic field between the sensors 14,16,18. Forming the ratio of P₁(ω)/P₂(ω) from Eqns. 6,7, and solving for B/A, gives the following expression: $\begin{matrix} {{R \equiv \frac{B}{A}} = \frac{^{{- }\quad k_{r}x_{1}} - {\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{{- }\quad k_{r}x_{2}}}}{{\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{\quad k_{l}x_{2}}} - ^{\quad k_{l}x_{1}}}} & {{Eq}.\quad 8} \end{matrix}$

where R is defined as the reflection coefficient.

Forming the ratio of P₁(ω)/P₃(ω) from Eqs. 5 and 7 and solving for zero gives: $\begin{matrix} {{\frac{^{{- }\quad k_{r}x_{1}} + {R\quad e^{\quad k_{l}x_{1}}}}{^{{- }\quad k_{r}x_{3}} + {R\quad e^{\quad k_{l}x_{3}}}} - \left\lbrack \frac{P_{1}(\omega)}{P_{3}(\omega)} \right\rbrack} = 0} & {{Eq}.\quad 9} \end{matrix}$

where R=B/A is defined by Eq. 8 and kr and kl are related to a_(mix) as defined by Eq. 2. Eq. 9 may be solved numerically, for example, by defining an “error” or residual term as the magnitude of the left side of Eq.9, and iterating to minimize the error term. $\begin{matrix} {{m\quad a\quad {g\left\lbrack {\frac{^{{- }\quad k_{r}x_{1}} + {R\quad e^{\quad k_{l}x_{1}}}}{^{{- }\quad k_{r}x_{3}} + {R\quad e^{\quad k_{l}x_{3}}}} - \left\lbrack \frac{P_{1}(\omega)}{P_{3}(\omega)} \right\rbrack} \right\rbrack}} \equiv {E\quad r\quad r\quad o\quad r}} & {{Eq}.\quad 10} \end{matrix}$

For many applications in the oil industry, the axial velocity of the flow in the pipe is small compared to the speed of sound in the mixture (i.e., the axial Mach number M_(x) is small compared to one). For example, the axial velocity of the oil V_(oil) in a typical oil well is about 10 ft/sec and the speed of sound of oil a_(oil) is about 4,000 ft/sec. Thus, the Mach number Mx of a pure oil mixture is 0.0025 (V_(oil)/a_(oil)=10/4,000), and Eq. 2 reduces to approximately: $\begin{matrix} {k_{r} = {k_{l} = \frac{\omega}{a_{m\quad i\quad x}}}} & {{Eq}.\quad 11} \end{matrix}$

and the distinction between the wave numbers for the right and left traveling waves is eliminated. In that case (where Mx is negligible), since all of the variables in Eq. 10 are known except for a_(mix), the value for a_(mix) can be iteratively determined by evaluating the error term at a given frequency ω and varying a_(mix) until the error term goes to zero. The value of a_(mix) at which the magnitude of the error term equals zero (or is a minimum), corresponds to the correct value of the speed of sound of the mixture a_(mix). As Eq. 10 is a function of frequency ω, the speed of sound a_(mix) at which the error goes to zero is the same for each frequency ω evaluated (discussed more hereinafter). However, in practice, there may be some variation over certain frequencies due to other effects, e.g., pipe modes, non-acoustical pressure perturbation, discretization errors, etc., which may be filtered, windowed, averaged, etc. if desired (discussed more hereinafter). Furthermore, since each frequency is an independent measurement of the same parameter, the multiple measurements may be weighted averaged or filtered to provide a single more robust measurement of the speed of sound.

One example of how the speed of sound of the mixture a_(mix) in the pipe 12 may be used is to determine the volume fraction of the mixture. In particular, the speed of sound of a mixture a_(mix) of two fluids (where a fluid is defined herein as a liquid or a gas) in a pipe is in general related to the volume fraction of the two fluids. This relationship may be determined experimentally or analytically. For example, the speed of sound of a mixture may be expressed as follows: $\begin{matrix} {a_{m\quad i\quad x} = \sqrt{\frac{1 + {\frac{\rho_{1}}{\rho_{2}}\frac{h_{2}}{h_{1}}}}{\frac{1}{a_{1}^{2}} + {\frac{\rho_{1}}{\rho_{2}}\frac{h_{2}}{h_{1}}\frac{1}{a_{2}^{2}}}}}} & {{Eq}.\quad 12} \end{matrix}$

where a₁,a₂ are the known speeds of sound, ρ₁,ρ₂ are the known densities, and h₁,h₂ are the volume fractions of the two respective fluids, a_(mix) is the speed of sound of the mixture, and the densities ρ₁,ρ₂ of the two fluids are within about an order of magnitude (10:1) of each other. Other expressions relating the phase fraction to speed of sound may be used, being derived experimentally, analytically, or computationally.

Referring to FIG. 2, where the fluid is an oil/water mixture, a curve 10 shows the speed of sound of the mixture a_(mix) plotted as a function of water volume fraction using Eq. 12. For this illustrative example, the values used for density (ρ) and speed of sound (a) of oil and water are as follows:

Density(ρ): ρ_(water)=1,000 kg/m³; ρ_(oil)=700 kg/m³

Speed of sound (a): a_(water)=5,000 ft/sec; a_(oil)=4,000 ft/sec.

The subscripts 1,2 of Eq. 12 assigned to the parameters for each fluid is arbitrary provided the notation used is consistent. Thus, if the speed of sound of the mixture a_(mix) is measured, the oil/water fraction may be determined.

Referring to FIG. 3, to illustrate the concept by example, a transmission matrix model for the acoustics of an example pipe having 9 sections (or elements or segments) 1-9, an acoustic source 64, a radiation (or transmission) impedance ζ_(rad) (ζ_(rad)=P/ρ_(mix)a_(mix)μ_(mix)) where μ_(mix) is an acoustic perturbation; Mx=0, and where the pressures P₁,P₂,P₃ are measured across test sections 5-6 and 6-7. For this example, each element is 1 meter long.

Depending on the application, an explicit acoustic noise source may or may not be required, as the background acoustic noises within the pipe may provide sufficient excitation to enable a speed of sound measurement from existing ambient acoustic pressures. In an oil or gas well application, if the background acoustic noises are not sufficient, an acoustic noise source (not shown) may be placed at the surface of the well or within the well, provided the source is acoustically coupled to the test section 51 over which the speed of sound is measured.

Referring to FIG. 4, illustrations (a)-(c), an example of the axial properties of the mixture in the segments 1-9 of the pipe 12 is shown. The volume fraction of water h, the speed of sound of the mixture a_(mix), and the density of the mixture ρ_(mix) vary over the length of the pipe 12 and the test segments 5,6 (from 4-6 meters) between the pressure measurements P₁-P₃ have constant properties. In particular, the values for ρ_(mix),a_(mix),h_(water) for sections 1-9, respectively, are shown graphically in FIG. 4 and are as follows:

h _(water)=0.1,0.2,0.3,0.4,0.5,0.6,0.7,0.8,0.9;

ρ_(mix)=730,760,790,820,850,850,910,940,970(kg/m³);

 a _(mix)=4053,4111,4177,4251,4334,4334,4539,4667,4818(ft/sec);

Referring to FIGS. 5,6, the magnitude and phase of the ratio of the frequency based pressure signals P₁(ω)/P₂(ω) and P₁(ω)/P₃(ω) is shown for the model of FIG. 3 with the properties of FIG. 4 with 50% water in the test section and a radiation impedance of ζrad=1.0 corresponding to an infinitely long pipe with constant properties of ρ_(mix) and a_(mix) for section 9 and beyond.

Referring to FIG. 7, the error term of Eq. 10 using the frequency responses of FIGS. 5,6, is a family of curves, one curve for each frequency ω, where the value of the error is evaluated for values of a_(mix) varied from a_(water) (5,000 ft/sec) to a_(oil) (4,000 ft/sec) at each frequency and the frequency is varied from 5 to 200 Hz in 5 Hz increments. Other frequencies may be used if desired. The speed of sound a_(mix) where the error goes to zero (or is minimized) is the same for each frequency ω evaluated. In this case, the error is minimized at a point 70 when a_(mix) is 4335 ft/sec. From FIG. 2, for an oil/water mixture, an a_(mix) of 4335 ft/sec corresponds to a 50% water volume ratio in the test section that matches the water fraction of the model. Also, the sensitivity of a change in a_(mix) to a change in error varies based on the evaluation frequency. Thus, the performance may be optimized by evaluating a_(mix) at specific low sensitivity frequencies, such frequencies to be determined depending on the specific application and configuration.

Referring to FIGS. 8,9, for an radiation impedance ζrad=0.5, the magnitude and phase of the frequency responses (i.e., the ratio of frequency based pressure signals) P₁(ω)/P₂(ω) and P₁(ω)/P₃(ω) is shown for the model of FIG. 3 with constant properties across all sections 1-9 of 50% water fraction (h=0.5), density of mixture ρ_(mix)=850 kg/m³, and speed of sound of mixture a_(mix)=4334 ft/sec.

Referring to FIG. 12, for a 50% water fraction, the magnitude of the error term of Eq. 10 using the frequency responses of FIGS. 8, 9, is a family of curves, one curve for each frequency ω, where the value of a_(mix) is varied from a_(water) (5,000 ft/sec) to a_(oil) (4,000 ft/sec) at each frequency and is shown at four frequencies 50,100,150,200 Hz. As discussed hereinbefore, the speed of sound a_(mix) where the error goes to zero (or is minimized) is the same for each frequency ω evaluated. In this case, the error is minimized at a point 72 where a_(mix)=4334 ft/sec, which matches the value of a_(mix) shown in FIG. 7 for the same water fraction and different ζrad. From FIG. 2 (or Eq. 2), for an oil/water mixture, an a_(mix) of 4334 ft/sec corresponds to a 50% water volume ratio in the test section which corresponds to the water fraction of the model. This shows that the invention will accurately determine a_(mix) independent of the acoustic properties of the mixture outside the test sections and/or the termination impedances.

Referring to FIGS. 10,11, the magnitude and phase of the frequency responses (i.e., the ratio of the frequency based pressure signals) P₁(ω)/P₂(ω) and P₁(ω)/P₃(ω) is shown for the model of FIG. 3 with constant properties across all sections 1-9 of 5% water fraction (h=0.05), density of mixture ρ_(mix)=715 kg/m³, and speed of sound of mixture a_(mix)=4026 ft/sec, and a radiation impedance ζrad=0.5.

Referring to FIG. 12, for a 5% water fraction, the magnitude of the error term of Eq. 10 using the frequency responses of FIGS. 10,11, is a family of dashed curves, one curve for each frequency ω, where the value of a_(mix) is varied from a_(water) (5,000 ft/sec) to a_(oil) (4,000 ft/sec) at each frequency and is shown at four frequencies 50,100,150,200 Hz. As discussed hereinbefore, the speed of sound a_(mix) where the error goes to zero (or is minimized) is the same for each frequency ω evaluated. In this case, the error is minimized at a point 74 when a_(mix)=4026 ft/sec. From FIG. 1 (or Eq. 1), for an oil/water mixture, an a_(mix) of 4026 ft/sec corresponds to a 5% water volume ratio in the test section which corresponds to the water fraction of the model and, thus, verifies the results of the model.

Referring to FIG. 12, for both 5% and 50% water fraction, the sensitivity of a change in a_(mix) to a change in error varies based on the evaluation frequency. In particular, for this example, of the four frequencies shown, the error approaches zero with the largest slope (ΔError/Δa_(mix)) for the 200 Hz curve, thereby making it easier to detect the value where the error goes to zero, and thus the value of a_(mix). Thus, 200 Hz would likely be a robust frequency to use to determine the speed of sound in this example.

If the pressure sensors are equally spaced (i.e., x1−x2=x3−x2=Δx; or Δx1=Δx2=Δx) and the axial Mach number Mx is small compared to one (and thus, kr=kl=k), Eq. 10 may be solved for k (and thus a_(mix) ) in a closed-form solution as a function of the pressure frequency responses (or frequency based signal ratios) as follows: $\begin{matrix} {k = {\frac{\omega}{a_{m\quad i\quad x}} = {{\left\lbrack \frac{1}{\Delta \quad x} \right\rbrack \quad {{log}\left\lbrack \frac{\begin{matrix} {P_{12} + {P_{13}P_{12}} +} \\ \left( {P_{12}^{2} + {2P_{13}P_{12}^{2}} + {P_{13}^{2}P_{12}^{2}} - {4P_{13}^{2}}} \right)^{1/2} \end{matrix}}{2P_{13}} \right\rbrack}}}}} & {{Eq}.\quad 13} \end{matrix}$

Solving for a_(mix), gives: $\begin{matrix} {a_{m\quad i\quad x} = \frac{\omega}{\left\lbrack \frac{1}{\Delta \quad x} \right\rbrack \quad \quad {\log\left\lbrack \frac{\begin{matrix} {P_{12} + {P_{13}P_{12}} +} \\ \left( {P_{12}^{2} + {2P_{13}P_{12}^{2}} + {P_{13}^{2}P_{12}^{2}} - {4P_{13}^{2}}} \right)^{1/2} \end{matrix}}{2P_{13}} \right\rbrack}}} & {{Eq}.\quad 14} \end{matrix}$

where P₁₂=P₁(ω)/P₂(ω),P₁₃=P₁(ω)/P₃(ω), i is the square root of −1, and the result of the Log[] function is an imaginary number, yielding a real number for the speed of sound a_(mix).

The analytical solution to the Eq. 10 shown in Eqs. 13 and 14 is valid primarily for the frequencies for which the length of the test section 51 along the pipe 12 (i.e., x3−x1 or 2Δx for equally spaced sensors) is shorter than the wavelength λ of the acoustic waves to be measured. This restriction is due to multiple possible solutions to the Eq. 10. Alternative solutions to Eq. 10 for other frequency ranges may be derived using a variety of known techniques.

An alternative closed form solution for a_(mix) (in a trigonometric form) from the three pressure Eqs. 5-7, where the pressure sensors are equally spaced and Mx is negligible (i.e, kl=kr), is as follows. Forming the ratio [P₁(ω)+P₃(ω)]/P₂(ω) from Eqs. 5-7, gives the following expression: $\begin{matrix} {\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = \frac{{A\quad ^{{- }\quad k\quad x_{1}}} + {B\quad ^{{+ }\quad k\quad x_{1}}} + {A\quad ^{{- }\quad k\quad x_{3}}} + {B\quad ^{{+ {k}}\quad x_{3}}}}{{A\quad ^{{- }\quad k\quad x_{2}}} + {B\quad ^{{+ }\quad k\quad x_{2}}}}} & {{Eq}.\quad 15} \end{matrix}$

For equally spaced sensors, x1=0,x2=Δx, x3=2Δx (x1=0 for convenience only), which gives: $\begin{matrix} {\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = \frac{A + B + {A\quad ^{{- 2}\quad k\quad \Delta \quad x}} + {B\quad ^{{{+ 2}\iota \quad k\quad \Delta \quad x}}}}{{A\quad ^{{- }\quad k\quad \Delta \quad x}} + {B\quad ^{{+ }\quad k\quad \Delta \quad x}}}} & {{Eq}.\quad 16} \end{matrix}$

Dividing the numerator and denominator by A, gives: $\begin{matrix} {\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = \frac{1 + R + ^{{- 2}\quad k\quad \Delta \quad x} + {Re}^{{+ 2}\quad k\quad \Delta \quad x}}{^{{- }\quad k\quad \Delta \quad x} + {Re}^{{+ }\quad k\quad \Delta \quad x}}} & {{Eq}.\quad 17} \end{matrix}$

where R=B/A is defined by Eq. 8 with x1=0,x2=Δx, which gives: $\begin{matrix} {{{{{R \equiv \frac{B}{A}} = \frac{1 - {\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{{- }\quad k\quad \Delta \quad x}}}{{\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{\quad k\quad \Delta \quad x}} - 1}}{Plugging}\quad R\quad {into}\quad {{Eq}.\quad 17}},\quad {{gives}\text{:}}}\quad \quad} & {{Eq}.\quad 18} \\ {{{\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = \frac{1 + ^{{- 2}\quad k\quad \Delta \quad x} + \left\lbrack \frac{1 - {\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{{- }\quad k\quad \Delta \quad x}}}{{\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{\quad k\quad \Delta \quad x}} - 1} \right\rbrack + \left( {1 + ^{{+ 2}\quad k\quad \Delta \quad x}} \right)}{^{{- }\quad k\quad \Delta \quad x} + {\left\lbrack \frac{1 - {\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{{- }\quad k\quad \Delta \quad x}}}{{\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{\quad k\quad \Delta \quad x}} - 1} \right\rbrack ^{{+ }\quad k\quad \Delta \quad x}}}}{{{Simplifying}\quad {{Eq}.\quad 19}},\quad {{gives}\text{:}}}}\quad} & {{Eq}.\quad 19} \\ {\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = \frac{{\left( {{\frac{P_{1}}{P_{2}}^{{+ }\quad k\quad \Delta \quad x}} - 1} \right)\left( {1 + ^{{- 2}\quad k\quad \Delta \quad x}} \right)} + {\left( {1 - {\frac{P_{1}}{P_{2}}^{{- }\quad {kx}}}} \right)\left( {1 + ^{{+ 2}\quad k\quad \Delta \quad x}} \right)}}{{\left( {{\frac{P_{1}}{P_{2}}^{{+ }\quad k\quad \Delta \quad x}} - 1} \right)\left( ^{{- }\quad k\quad \Delta \quad x} \right)} + {\left( {1 - {\frac{P_{1}}{P_{2}}^{{- }\quad {kx}}}} \right)\left( ^{{+ }\quad k\quad \Delta \quad x} \right)}}} & {{Eq}.\quad 20} \end{matrix}$

Distributing terms and simplifying, gives: $\begin{matrix} {\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = \frac{{- ^{{- 2}\quad k\quad \Delta \quad x}} + ^{{+ 2}\quad k\quad \Delta \quad x}}{{- ^{{- }\quad k\quad \Delta \quad x}} + ^{{+ }\quad k\quad \Delta \quad x}}} & {{Eq}.\quad 21} \end{matrix}$

Using the relation between exponents and the sine function, gives: $\begin{matrix} {\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = {\frac{2\quad {\sin \left( {2k\quad \Delta \quad x} \right)}}{2\quad {\sin \left( {k\quad x} \right)}} = \frac{2\quad {\sin \left( {k\quad x} \right)}{\cos ({kx})}}{\sin ({kx})}}} & {{Eq}.\quad 22} \end{matrix}$

Simplifying and substituting k=ω/a_(mix), gives: $\begin{matrix} {\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = {{2\quad {\cos \left( {k\quad \Delta \quad x} \right)}} = {2\quad {\cos \left( \frac{{\omega\Delta}\quad x}{a_{mix}} \right)}}}} & {{Eq}.\quad 23} \end{matrix}$

Eq. 23 is particularly useful due to its simple geometric form, from which a_(mix) can be easily interpreted. In particular, a_(mix) can be determined directly by inspection from a digital signal analyzer (or other similar instrument) set up to provide a display indicative of the left side of Eq. 23, which will be a cosine curve from which a_(mix) may be readily obtained. For example, at the zero crossing of the cosine wave, Eq. 23 will be equal to zero and a_(mix) will be equal to 2ωΔX/π. Alternatively, Eq. 23 may be used to determine amix using an iterative approach where a measured function is calculated from the left side of Eq. 23 (using the measured pressures) and compared to a cosine curve of the right side of Eq. 23 where amix is varied until it substantially matches the measured function. Various other curve fitting, parameter identification, and/or minimum error or solution techniques may be used to determine the value of amix that provides the best fit to satisfy Eq. 23.

Solving Eq. 23 for a_(mix), gives the following closed-form solution: $\begin{matrix} {a_{mix} = {\frac{\omega \quad \Delta \quad x}{\cos^{- 1}\left( \frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{2{P_{2}(\omega)}} \right)} = \frac{\omega \quad \Delta \quad x}{\cos^{- 1}\frac{1}{2}\left( {\frac{P_{1}(\omega)}{P_{2}(\omega)} + \frac{P_{3}(\omega)}{P_{2}(\omega)}} \right)}}} & {{Eq}.\quad 24} \end{matrix}$

Referring to FIG. 41, a graph of speed of sound (a_(mix)) versus water cut is shown where a_(mix) is calculated using Eq. 23 as described hereinbefore. FIG. 41 is for a Schedule 160 steel pipe having a 2 inch ID, ΔX=2 ft even spacing between three axial sensing locations, each sensor being a piezo-electric ac pressure sensor, there being four evenly circumferentially spaced sensors at each axial sensing location. The line 452 shows the theoretical value for water cut based on Eq. 12 and FIG. 2 discussed hereinbefore, and the circles are the calculated values for a_(mix).

Alternatively, Eq. 9 may be written in trigonometric form for arbitrary spacing between the pressure sensors and where Mx is negligible (kl=kr), as follows: $\begin{matrix} {{{\sin \left( {\frac{\omega}{a_{mix}}\left( {x_{3} - x_{1}} \right)} \right)} - {P_{32}{\sin \left( {\frac{\omega}{a_{mix}}\left( {x_{2} - x_{1}} \right)} \right)}} - {P_{12}{\sin \left( {\frac{\omega}{a_{mix}}\left( {x_{3} - x_{2}} \right)} \right)}}} = 0} & {{Eq}.\quad 25} \end{matrix}$

where P₃₂=P₃(ω)/P₂(ω) and P₁₂=P₁(ω)/P₂(ω).

Referring to FIGS. 13,14, if Mach number Mx is not negligible and/or is desired to be calculated, the value of Mx and a_(mix) where the error term of Eq. 10 is zero can be uniquely determined from Eq. 10 for a given water fraction. In particular, for a given % water fraction, there is a unique value indicated by points 90,92 for 5% and 50% water cut, respectively. Known software search algorithms may be used to vary a_(mix) and Mx over predetermined ranges to find the value of Mx and a_(mix) where the error=0 (discussed more hereinafter).

Referring to FIG. 15, the calculation logic 40 begins at a step 100 where P₁₂ is calculated as the ratio of P₁(ω)/P₂(ω), and a step 102 where P₁₃ is calculated as the ratio of P₁(ω)/P₃(ω). Next a step 103 determines whether the Mach number Mx of the mixture is negligible (or whether it is desirable to calculate Mx, i.e. for cases where Mx is not negligible, as set forth herein below with reference to “A” and FIG. 16). If Mx is negligible, a step 104 determines if the sensors 14,16,18 are equally spaced (i.e., x1−x2=x2−x3=Δx). If equally spaced sensors, steps 106 set initial values for ω=ω1 (e.g., 100 Hz) and a counter n=1. Next, a step 108 calculates a_(mix)(n) from the closed form solution of Eq. 14. Then, a step 110 checks whether the logic 40 has calculated a_(mix) at a predetermined number of frequencies, e.g., 10. If n is not greater than 10, steps 112,114, increments the counter n by one and increases the frequency ω by a predetermined amount (e.g., 10 Hz) and the step 108 is repeated. If the logic 40 has calculated a_(mix) at 10 frequencies, the result of the step 116 would be yes and the logic 40 goes to a step 116 which determines an average value for a_(mix) using the values of a_(mix)(n) over the 10 frequencies, and the logic 40 exits.

If the sensors are not equally spaced, a series of steps 150 are performed starting with steps 120 set x1,x2,x3 to the current pressure sensor spacing, and set initial values for ω=ω1 (e.g., 100 Hz) and the counter n=1. Next, a step 122 sets a_(mix)=a_(mix−min) (e.g., a_(oil)=4000 ft/sec) and a step 124 calculates the error term from Eq. 10. Then, a step 126 checks whether error=0. If the error does not equal zero, a_(mix) is incremented by a predetermined amount in step 128 and the logic 40 goes back to step 124.

If the error=0 (or a minimum) in step 126, a step 130 sets a_(mix)(n)=a_(mix). Next, a step 132 checks whether n is greater than or equal to 10. If not, a step 134 increments n by one and a step 136 increases the frequency ω by a predetermined amount (e.g., 10 Hz) and continues at step 122 as shown in FIG. 15. If n is greater than or equal to 10, a step 138 calculates an average value for a_(mix) over the 10 frequencies, and the logic 40 ends.

Referring to FIG. 16, if the Mach number Mx is not negligible, steps 200,202,204 sets initial conditions: ω=ω1 (e.g., 100 Hz); Mx=Mx−min (e.g., 0); a_(mix)=a_(mix−min) (e.g., a_(oil)=4000 ft/sec). Then, a step 206 calculates the error term of Eq. 10 at a step 202. Next, a step 208 checks whether the error=0 (or a minimum). If not, a step 210 checks whether a_(mix)=a_(mix−max) (e.g., a_(water)=5000 ft/sec).

If the result of step 210 is no, a step 212 increases a_(mix) by a predetermined amount (e.g., 1 ft/sec) and the logic goes back to step 206. If the result of step 210 is yes, a step 214 increases Mx by a predetermined amount (e.g., 1) and the logic goes back to step 204.

When step 208 indicates error=0 (or a minimum), a step 216 sets a_(mix)(n)=a_(mix) and Mx(n)=Mx, and a step 218 checks whether the values of a_(mix) and Mx have been calculated at 10 different frequencies. If not, a step 220 increments the counter n by one and a step 222 increases the value of the frequency ω by a predetermined amount (e.g., 10 Hz), and the logic goes back to step 202. If the values of a_(mix) and Mx have been calculated at 10 different frequencies (i.e., n is equal to 10), a step 224 calculates a average values for a_(mix)(n) and Mx(n) at the 10 different frequencies to calculate a_(mix) and Mx, and the logic exists. The value for a_(mix) above is similar to that shown in FIGS. 13,14, discussed hereinbefore, where the final value of a_(mix) are the points 90,92 where the error equals zero.

Instead of calculating an average value for a_(mix) in steps 116,138, 224, a_(mix) may be calculated by filtering or windowing a_(mix)(n), from predetermined frequencies. The number of frequencies and the frequencies evaluated may be any desired number and values. Also, instead of calculating a_(mix) and/or Mx at more than one frequency, it may be calculated at only one frequency. Further, the logic shown in FIGS. 15,16 is one of many possible algorithms to calculate a_(mix) using the teachings herein.

Referring to FIGS. 1 and 18, the compliance (or flexibility) of the pipe 12 (or conduit) in the sensing region may influence the accuracy or interpretation of the measured speed of sound a_(mix) of the mixture in two primary ways.

Regarding the first way, referring to FIG. 18, flexing of the pipe 12 in the sensing region reduces the measured speed of sound a_(mix) from the sound in an unbounded domain. The sound speed in an unbounded domain (infinite media) is a property that is closely linked with the fluid properties. In particular, the influence of pipe wall thickness (or compliance of the pipe) on measured speed of sound due reduction in the speed of sound for a pipe having a 2 inch nominal diameter and having 100% water (ρ_(w)=1,000 kg/m³; a_(w)=5,000 ft/sec) inside the pipe and a vacuum (or air) outside the pipe diameter, is shown. The speed of sound of water in an infinitely rigid pipe (i.e., infinite modulus) is indicated by a flat curve 350, and the speed of sound of water in a steel pipe is indicated by a curve 352. A point 354 on the curve 352 indicates the value of the speed of sound of about 4768 ft/sec for a Schedule 80 steel pipe. Accordingly, the thicker the pipe wall, the closer the speed of sound approaches the value of 5,000 ft/sec for an infinitely rigid pipe.

The errors (or boundary effects) shown in FIG. 18 introduced into the measurements by a non-rigid (or compliant) pipe 12 can be calibrated and corrected for to accurately determine the speed of sound in the fluid in an unbounded media. Thus, in this case, while the system (pipe) does modify the propagation velocity, such velocity can be mapped to the propagation velocity in an infinite media in a predictable fashion.

In particular, for fluids contained in a compliant pipe, the propagation velocity of compression waves is influenced by the structural properties of the pipe. For a fluid contained in the pipe 12 surrounded with a fluid of negligible acoustic impedance (ρα), the propagation velocity is related to the infinite fluid domain speed of sound and the structural properties via the following relation: $\begin{matrix} {\frac{1}{\rho_{mix}a_{measured}^{2}} = {{\frac{1}{\rho_{mix}a_{mix}^{2}} + {\sigma \quad {where}\quad \sigma}} \equiv \frac{2R}{Et}}} & {{Eq}.\quad 26} \end{matrix}$

where R=the pipe radius, t is the pipe wall thickness, ρ_(mix) is the density of the mixture (or fluid), a_(mix) is the actual speed of sound of the mixture, a_(measured) is the measured speed of sound of the mixture contained in the pipe 12, and E is the Young's modulus for the pipe material. Eq. 26 holds primarily for frequencies where the wavelength of the acoustics is long (e.g., greater than about 2 to 1) compared to the diameter of the pipe and for frequencies which are low compared to the natural frequency of the breathing mode of the pipe. Eq. 26 also applies primarily to wavelengths which are long enough such that hoop stiffness dominates the radial deflections of the pipe.

For FIG. 18, the curve 352 (for 100% water) would be one of a family of curves for various different oil/water mixtures. For Eq. 26, the terms may be defined in terms of the density of each constituent, and the volumetric phase fraction as follows: $\frac{1}{\rho_{mix}a_{mix}^{2}} = {{\sum\limits_{i = 1}^{N}\quad {\frac{\varphi_{i}}{\rho_{i}a_{i}^{2}}\quad {where}\text{:}\quad \rho_{mix}}} = {{\sum\limits_{i = 1}^{N}{\varphi_{i}\rho_{i}\quad {and}\quad {\sum\limits_{i = 1}^{N}\varphi_{i}}}} = 1}}$

where ρ_(i) is the density of the i^(th) constituent of a multi-component mixture, α_(i) is the sound speed of the i^(th) constituent of the mixture, Φ_(i) is the volumetric phase fraction of the i^(th) constituent of the mixture, and N is the number of components of the mixture. Knowing the pipe properties, the densities and the sound speed (in an infinite domain) of the individual constituents, and the measured sound speed of the mixture, Eq. 26 can be solved for a_(mix). Thus, a_(mix) can be determined for a compliant pipe. The calibration of the pipe can be derived from other equations or from a variety of other means, such as analytical, experimental, or computational.

For certain types of pressure sensors, e.g., pipe strain sensors, accelerometers, velocity sensors or displacement sensors, discussed hereinafter, it may be desirable for the pipe 12 to exhibit a certain amount of pipe compliance.

Alternatively, to minimize these error effects (and the need for the corresponding calibration) caused by pipe compliance, the axial test section 51 of the pipe 12 along where the sensors 14,16,18 are located may be made as rigid as possible. To achieve the desired rigidity, the thickness of the wall 53 of the test section 51 may be made to have a predetermined thickness, or the test section 51 may be made of a very rigid material, e.g., steel, titanium, Kevlar®, ceramic, or other material with a high modulus.

Regarding the second way, if the pipe 12 is compliant and acoustically coupled to fluids and materials outside the pipe 12 in the sensing region, such as the annulus fluid, casing, rock formations, etc., the acoustic properties of these fluids and materials outside the pipe 12 diameter may influence the measured speed of sound. Because the acoustic properties of such fluids and materials are variable and unknown, their affect on measured speed of sound cannot be robustly corrected by calibration (nor mapped to the propagation velocity in an infinite media in a predictable fashion).

Referring to FIG. 20, to alleviate this effect, an outer isolation sleeve 410 (or sheath, shell, housing, or cover) which is attached to the outer surface of pipe 12 over where the pressure sensors 14,16,18 are located on the pipe 12. The sleeve 410 forms a closed chamber 412 between the pipe 12 and the sleeve 410. We have found that when the chamber 412 is filled with a gas such as air, the acoustic energy in the pipe is not acoustically coupled to fluids and materials outside the pipe 12 in the sensing region. As such, for a compliant pipe the speed of sound can be calibrated to the actual speed of sound in the fluid in the pipe 12 as discussed hereinbefore. The sleeve 410 is similar to that U.S. application Ser. No. 09/344,070, entitled “Measurement of Propagating Acoustic Waves in Compliant Pipes”, filed Jun. 25, 1999, which is incorporated herein by reference.

Referring to FIG. 19, instead of single point pressure sensors 14,16,18, at the axial locations x1,x2,x3 along the pipe 12, two or more pressure sensors, e.g., four sensors 400, 402, 404, 406, may be used around the circumference of the pipe 12 at each of the axial locations x1,x2,x3. The signals from the pressure sensors, 400, 402, 404, 406 around the circumference at a given axial location may be averaged to provide a cross-sectional (or circumference) averaged unsteady acoustic pressure measurement. Other numbers of acoustic pressure sensors and annular spacing may be used. Averaging multiple annular pressure sensors reduces noises from disturbances and pipe vibrations and other sources of noise not related to the one-dimensional acoustic pressure waves in the pipe 12, thereby creating a spatial array of pressure sensors to help characterize the one-dimensional sound field within the pipe 12.

The pressure sensors 14,16,18 described herein may be any type of pressure sensor, capable of measuring the unsteady (or ac or dynamic ) pressures within a pipe, such as piezoelectric, optical, capacitive, resistive (e.g., Wheatstone bridge), accelerometers (or geophones), velocity measuring devices, displacement measuring devices, etc. If optical pressure sensors are used, the sensors 14,16,18 may be Bragg grating based pressure sensors, such as that described in U.S. patent application Ser. No. 08/925,598, entitled “High Sensitivity Fiber Optic Pressure Sensor For Use In Harsh Environments”, filed Sep. 8, 1997, now U.S. Pat. No. 6,016,702. Alternatively, the sensors 14,16,18 may be electrical or optical strain gages attached to or embedded in the outer or inner wall of the pipe which measure pipe wall strain, including microphones, hydrophones, or any other sensor capable of measuring the unsteady pressures within the pipe 12. In an embodiment of the present invention that utilizes fiber optics as the pressure sensors 14,16,18, they may be connected individually or may be multiplexed along one or more optical fibers using wavelength division multiplexing (WDM), time division multiplexing (TDM), or any other optical multiplexing techniques (discussed more hereinafter).

Such harsh environments are typically found in the industrial process area and include sensor exposure to acids, caustics, nuclear energy, electromagnetic interference and exposure to explosive vapors among other hazards. Because the sensor is glass based it is chemically impervious to most industrial process related chemicals. Further because the sensor of the present invention uses light for signal transmission it does not require any electrical power and as such is not influenced by electromagnetic fields and cannot create arcing or explosions when used in the presence of flammable vapors. In addition the sensor of the present invention has no moving parts, such as a bellows, which makes the device more reliable and less susceptible to system hysteresis found in other mechanical pressure sensors that utilize diaphragms bellows or other displacement type devices.

Referring to FIG. 21, if a strain gage is used as one or more of the pressure sensors 14,16,18, it may measure the unsteady (or dynamic or ac) pressure variations Pin inside the pipe 12 by measuring the elastic expansion and contraction, as represented by arrows 350, of the diameter (and thus the circumference as represented by arrows 351) of the pipe 12. In general, the strain gages would measure the pipe wall deflection in any direction in response to unsteady pressure signals inside the pipe 12. The elastic expansion and contraction of pipe 12 is measured at the location of the strain gage as the internal pressure P_(in) changes, and thus measures the local strain (axial strain, hoop strain or off axis strain), caused by deflections in the directions indicated by arrows 351, on the pipe 12. The amount of change in the circumference is variously determined by the hoop strength of the pipe 12, the internal pressure P_(in), the external pressure P_(out) outside the pipe 12, the thickness T_(w) of the pipe wall 352, and the rigidity or modulus of the pipe material. Thus, the thickness of the pipe wall 352 and the pipe material in the sensor sections 51 (FIG. 1) may be set based on the desired sensitivity of sensors 14,16,18, and other factors and may be different from the wall thickness or material of the pipe 12 outside the sensing region 51.

Still with reference to FIG. 21 and FIG. 1, if an accelerometer is used as one or more of the pressure sensors 14,16,18, it may measure the unsteady (or dynamic or ac) pressure variations P_(in) inside the pipe 12 by measuring the acceleration of the surface of pipe 12 in a radial direction, as represented by arrows 350. The acceleration of the surface of pipe 12 is measured at the location of the accelerometer as the internal pressure P_(in) changes and thus measures the local elastic dynamic radial response of the wall 352 of the pipe. The magnitude of the acceleration is variously determined by the hoop strength of the pipe 12, the internal pressure P_(in), the external pressure P_(out) outside the pipe 12, the thickness T_(w) of the pipe wall 352, and the rigidity or modulus of the pipe material. Thus, the thickness of the pipe wall 352 and the pipe material in the sensing section 51 (FIG. 1) may be set based on the desired sensitivity of sensors 14,16,18 and other factors and may be different from the wall thickness or material of the pipe 12 outside the sensing region 14. Alternatively, the pressure sensors 14,16,18 may comprise a radial velocity or displacement measurement device capable of measuring the radial displacement characteristics of wall 352 of pipe 12 in response to pressure changes caused by unsteady pressure signals in the pipe 12. The accelerometer, velocity or displacement sensors may be similar to those described in commonly-owned copending U.S. patent application, Ser. No. 09/344,069, entitled “Displacement Based Pressure Sensor Measuring Unsteady Pressure in a Pipe”, filed Jun. 25, 1999 and incorporated herein by reference.

Referring to FIGS. 22,23,24, if an optical strain gage is used, the ac pressure sensors 14,16,18 may be configured using an optical fiber 300 that is coiled or wrapped around and attached to the pipe 12 at each of the pressure sensor locations as indicated by the coils or wraps 302,304,306 for the pressures P₁,P₂,P₃, respectively. The fiber wraps 302,304,306 are wrapped around the pipe 12 such that the length of each of the fiber wraps 302,304,306 changes with changes in the pipe hoop strain in response to unsteady pressure variations within the pipe 12 and thus internal pipe pressure is measured at the respective axial location. Such fiber length changes are measured using known optical measurement techniques as discussed hereinafter. Each of the wraps measure substantially the circumferentially averaged pressure within the pipe 12 at a corresponding axial location on the pipe 12. Also, the wraps provide axially averaged pressure over the axial length of a given wrap. While the structure of the pipe 12 provides some spatial filtering of short wavelength disturbances, we have found that the basic principle of operation of the invention remains substantially the same as that for the point sensors described hereinbefore.

Referring to FIG. 22, for embodiments of the present invention where the wraps 302,304,306 are connected in series, pairs of Bragg gratings (310,312), (314,316), (318,320) may be located along the fiber 300 at opposite ends of each of the wraps 302,304,306, respectively. The grating pairs are used to multiplex the pressure signals P₁,P₂,P₃ to identify the individual wraps from optical return signals. The first pair of gratings 310,312 around the wrap 302 may have a common reflection wavelength λ₁, and the second pair of gratings 314,316 around the wrap 304 may have a common reflection wavelength λ₂, but different from that of the first pair of gratings 310,312. Similarly, the third pair of gratings 318,320 around the wrap 306 have a common reflection wavelength λ₃, which is different from λ₁,λ₂.

Referring to FIG. 23, instead of having a different pair of reflection wavelengths associated with each wrap, a series of Bragg gratings 360, 362, 364, 366 with only one grating between each of the wraps 302, 304, 306 may be used each having a common reflection wavelength λ₁.

Referring to FIGS. 22 and 23 the wraps 302, 304, 306 with the gratings 310, 312, 314, 316, 318, 320 (FIG. 22) or with the gratings 360, 362, 364, 366 (FIG. 23) may be configured in numerous known ways to precisely measure the fiber length or change in fiber length, such as an interferometric, Fabry Perot, time-of-flight, or other known arrangements. One example of time-of-flight (or Time-Division-Multiplexing; TDM) would be where an optical pulse having a wavelength is launched down the fiber 300 and a series of optical pulses are reflected back along the fiber 300. The length of each wrap can then be determined by the time delay between each return pulse.

While the gratings 310, 312, 314, 316, 318, 320 are shown oriented axially with respect to pipe 12, in FIGS. 22,23, they may be oriented along the pipe 12 axially, circumferentially, or in any other orientations. Depending on the orientation, the grating may measure deformations in the pipe wall 352 with varying levels of sensitivity. If the grating reflection wavelength varies with internal pressure changes, such variation may be desired for certain configurations (e.g., fiber lasers) or may be compensated for in the optical instrumentation for other configurations, e.g., by allowing for a predetermined range in reflection wavelength shift for each pair of gratings. Alternatively, instead of each of the wraps being connected in series, they may be connected in parallel, e.g., by using optical couplers (not shown) prior to each of the wraps, each coupled to the common fiber 300.

Referring to FIG. 24, alternatively, the sensors 14, 16, 18 may also be formed as a purely interferometric sensor by wrapping the pipe 12 with the wraps 302, 304, 306 without using Bragg gratings where separate fibers 330,332,334 may be fed to the separate wraps 302,304,306, respectively. In this particular embodiment, known interferometric techniques may be used to determine the length or change in length of the fiber 10 around the pipe 12 due to pressure changes, such as Mach Zehnder or Michaelson Interferometric techniques, such as those set forth in U.S. patent application Ser. No. 09/726,059, titled “Method and Apparatus for Interrogating Fiber Optic Sensors ” filed Nov. 29, 2000. The inteferometric wraps may be multiplexed such as is described in Dandridge, et al, “Fiber Optic Sensors for Navy Applications”, IEEE, February 1991, or Dandridge, et al, “Multiplexed Intereferometric Fiber Sensor Arrays”, SPIE, Vol. 1586, 1991, pp 176-183. Other techniques to determine the change in fiber length may be used. Also, reference optical coils (not shown) may be used for certain interferometric approaches and may also be located on or around the pipe 12 but may be designed to be insensitive to pressure variations.

Referring to FIGS. 25 and 26, instead of the wraps 302,304,306 being optical fiber coils wrapped completely around the pipe 12, the wraps 302,304,306 may have alternative geometries, such as a “radiator coil” geometry (FIG. 25) or a “race-track” geometry (FIG. 26), which are shown in a side view as if the pipe 12 is cut axially and laid flat. In this particular embodiment, the wraps 302-206 are not necessarily wrapped 360 degrees around the pipe, but may be disposed over a predetermined portion of the circumference of the pipe 12, and have a length long enough to optically detect the changes to the pipe circumference. Other geometries for the wraps may be used if desired. Also, for any geometry of the wraps described herein, more than one layer of fiber may be used depending on the overall fiber length desired. The desired axial length of any particular wrap is set depending on the characteristics of the ac pressure desired to be measured, for example the axial length of the pressure disturbance caused by a vortex to be measured.

Referring to FIGS. 27 and 28, embodiments of the present invention include configurations wherein instead of using the wraps 302, 304, 306, the fiber 300 may have shorter sections that are disposed around at least a portion of the circumference of the pipe 12 that can optically detect changes to the pipe circumference. It is further within the scope of the present invention that sensors may comprise an optical fiber 300 disposed in a helical pattern (not shown) about pipe 12. As discussed herein above, the orientation of the strain sensing element will vary the sensitivity to deflections in pipe wall 352 deformations caused by unsteady pressure signals in the pipe 12.

Referring to FIG. 27, in particular, the pairs of Bragg gratings (310,312), (314,316), (318,320) are located along the fiber 300 with sections 380, 382, 384 of the fiber 300 between each of the grating pairs, respectively. In that case, known Fabry Perot, interferometric, time-of-flight or fiber laser sensing techniques may be used to measure the strain in the pipe.

Referring to FIG. 28, alternatively, individual gratings 370, 372, 374 may be disposed on the pipe and used to sense the unsteady variations in strain in the pipe 12 (and thus the unsteady pressure within the pipe) at the sensing locations. When a single grating is used per sensor, the grating reflection wavelength shift will be indicative of changes in pipe diameter and thus pressure.

Any other technique or configuration for an optical strain gage may be used. The type of optical strain gage technique and optical signal analysis approach is not critical to the present invention, and the scope of the invention is not intended to be limited to any particular technique or approach.

For any of the embodiments described herein, the pressure sensors, including electrical strain gages, optical fibers and/or gratings among others as described herein, may be attached to the pipe by adhesive, glue, epoxy, tape or other suitable attachment means to ensure suitable contact between the sensor and the pipe 12. The sensors may alternatively be removable or permanently attached via known mechanical techniques such as mechanical fastener, spring loaded, clamped, clam shell arrangement, strapping or other equivalents. Alternatively, the strain gages, including optical fibers and/or gratings, may be embedded in a composite pipe. If desired, for certain applications, the gratings may be detached from (or strain or acoustically isolated from) the pipe 12 if desired.

Referring to FIGS. 29,30, it is also within the scope of the present invention that any other strain sensing technique may be used to measure the variations in strain in the pipe, such as highly sensitive piezoelectric, electronic or electric, strain gages attached to or embedded in the pipe 12. Referring to FIG. 29, different known configurations of highly sensitive piezoelectric strain gages are shown and may comprise foil type gages. Referring to FIG. 30, an embodiment of the present invention is shown wherein pressure sensors 14, 16, 18 comprise strain gages 340. In this particular embodiment strain gages 340 are disposed about a predetermined portion of the circumference of pipe 12. The axial placement of and separation distance ΔX₁,ΔX₂ between the pressure sensors 14, 16, 18 are determined as described herein above. Referring to FIGS. 31-33, instead of measuring the unsteady pressures P₁-P₃ on the exterior of the pipe 12, the invention will also work when the unsteady pressures are measured inside the pipe 12. In particular, the pressure sensors 14,16,18 that measure the pressures P₁,P₂,P₃ may be located anywhere within the pipe 12 and any technique may be used to measure the unsteady pressures inside the pipe 12.

Referring to FIGS. 34-36, the invention may also measure the speed of sound of a mixture flowing outside a pipe or tube 425. In that case, the tube 425 may be placed within the pipe 12 and the pressures P₁-P₃ measured at the outside of the tube 425. Any technique may be used to measure the unsteady pressures P₁-P₃ outside the tube 425. Referring to FIG. 34, for example, the tube 425 may have the optical wraps 302, 304, 306 wrapped around the tube 425 at each sensing location. Alternatively, any of the strain measurement or displacement, velocity or accelerometer sensors or techniques described herein may be used on the tube 425. Referring to FIG. 35, alternatively, the pressures P₁-P₃ may be measured using direct pressure measurement sensors or techniques described herein. Any other type of unsteady pressure sensors 14, 16, 18 may be used to measure the unsteady pressures within the pipe 12.

Alternatively, referring to FIG. 36, hydrophones 430, 432, 434 may be used to sense the unsteady pressures within the pipe 12. In that case, the hydrophones 430, 432, 434 may be located in the tube 425 for ease of deployment or for other reasons. The hydrophones 430, 432, 434 may be fiber optic, electronic, piezoelectric or other types of hydrophones. If fiber optic hydrophones are used, the hydrophones 430, 432, 434 may be connected in series or parallel along the common optical fiber 300.

The tube 425 may be made of any material that allows the unsteady pressure sensors to measure the pressures P₁-P₃ and may be hollow, solid, or gas filled or fluid filled. One example of a dynamic pressure sensor is described in co-pending commonly-owned U.S. patent application, Ser. No. 09/326,097 entitled “Mandrel Wound Fiber Optic Pressure Sensor”, filed Jun. 4, 1999. Also, the end 422 of the tube 425 is closed and thus the flow path would be around the end 422 as indicated by lines 424. For oil and gas well applications, the tube 425 may be coiled tubing or equivalent deployment tool having the pressure sensors 14, 16, 18 for sensing P₁-P₃ inside the tubing 425. Alternatively the tube 425 may also include a bluff or rounded shaped end as indicated by dashed line 420.

Referring to FIG. 17, there is shown an embodiment of the present invention in a typical industrial processing application, the sensing section 51 may be connected to or part of process tubing 502 (analogous to the pipe 12 in the test section 51) within an industrial process control system 500. The isolation sleeve 410 may be located over the sensors 14, 16, 18 as discussed hereinbefore and attached to the pipe 502 at the axial ends to protect the sensors 14, 16, 18 (or fibers) from damage during deployment, use, or retrieval, and/or to help isolate the sensors from acoustic external pressure effects that may exist outside the pipe 502, and/or to help isolate ac pressures in the pipe 502 from ac pressures outside the pipe 502. The advantages and effect of the isolation sleeve 410, as well as other isolation techniques, are described in commonly owned copending U.S. patent application Ser. No. 09/344,070, entitled “Measurement of Propagating Acoustic Waves in Compliant Pipes” incorporated herein by reference in its entirety. The sensors 14, 16, 18 are connected to a cable 506 which may comprise the optical fiber 300 (FIGS. 22,23,27,28) and is connected to a transceiver/converter 510 of the control system 500.

When optical sensors are used, the transceiver/converter 510 may be used to receive and transmit optical signals 504 to the sensors 14, 16, 18 and provides output signals indicative of the pressure P₁-P₃ at the sensors 14, 16, 18 on the lines, 20, 22, 24, respectively. Also, the transceiver/ converter 510 may be part of the Fluid Parameter Logic 60. The transceiver/converter 510 may be any device that performs the corresponding functions described herein. In particular, the transceiver/converter 510 together with the optical sensors described hereinbefore may use any type of optical grating-based measurement technique, e.g., scanning interferometric, scanning Fabry Perot (resonator, cavity, interferometer or other known Fabry Perot arrangement), acousto-optic-tuned filter (AOTF), optical filter, time-of-flight, and may use WDM and/or TDM, etc., having sufficient sensitivity to measure the ac pressures within the pipe.

A plurality of the sensors 10 of the present invention may be connected to a common cable and multiplexed together using any known multiplexing technique by connecting end 511 to other sensors (not shown). For instance, it is contemplated that the various embodiments of the sensor 10 of the present invention include the capability being multiplexed as well as capable of communication with various protocols and systems currently in use in the industrial sensing area. For instance, and with reference to FIG. 17 there is shown a portion of a process control system 500 incorporating a sensor 10 in accordance with the present invention. Fluid parameter logic 60 communicates signals Mx, amix, and % Composition along lines 59, 46, 50 to control device 70, a computer or micro-processor for example, where the information may be used to control the fluid characteristics in pipe 502 through known controls means such as a pump, valve, throttle, etc. (not shown). In certain embodiments of control system 500 and with appropriate electro-optical conversion of the sensor return signal to a conventional 4-20 mA signal the signal can be combined with other control devices and sensors at control device 70 via separate electrical lines. In this particular embodiment the communication from the fiber optic sensor is performed with a 4-20 mA analog signal, and the open protocol HART®. (Highway Addressable Remote Transducer) digital communications format. Similarly, communication from the fiber optic sensor 10 may also be performed with open and interoperable protocol FOUNDATION™ Fieldbus that provides a digital communication link among intelligent field level and control devices via electrical lines. The control device 70 can be configured for use with other process protocols, including Device Bus, Sensor Bus, Profibus, the ethernet, and others in use throughout the world. The use of feedthroughs 511, as shown in FIG. 17, make the sensor 10 of the present invention uniquely qualified for industrial applications requiring multiple sensors. The use of sensors having feedthroughs in a large multi-point process enables connectivity to the multiple sensors through a single fiber optic cable. Electronic sensors of the prior art require dedicated wiring to the sensor and back to the instrumentation. For instance, a typical industrial process control system that utilizes electronic flowmeters of the prior art requires an electrical process loop to facilitate both a power signal to the transmitters and bi-directional communication, and can be constructed in accordance with a number of the aforementioned process communication protocols.

In operation, industrial process uses for the present invention include reverse osmosis, coking, general refining uses, in-line pressure sensors for emissions monitoring, sensors for monitoring hydrogen, combustion control, gas composition analysis, distributed sensors in tank gauging, multi-phase computational fluid dynamics, instrumentation of multiphase flows, among others.

It should be understood that the present invention can be used to measure fluid volume fractions of a mixture of any number of fluids in which the speed of sound of the mixture a_(mix) is related to (or is substantially determined by), the volume fractions of two constituents of the mixture, e.g., oil/water, oil/gas, water/gas. The present invention can be used to measure the speed of sound of any mixture and can then be used in combination with other known quantities to derive phase content of mixtures with multiple (more than two) constituents.

Further, the present invention can be used to measure any parameter (or characteristic) of any mixture of one or more fluids in which such parameter is related to the speed of sound of the mixture a_(mix), e.g., fluid fraction, temperature, salinity, mineral content, sand particles, slugs, pipe properties, etc. or any other parameter of the mixture that is related to the speed of sound of the mixture. Accordingly, the logic 48 (FIG. 1) may convert a_(mix) to such parameter(s).

Further, the invention will work independent of the direction of the flow or the amount of flow of the fluid(s) in the pipe, and whether or not there is flow in the pipe. Also, independent of the location, characteristics and/or direction(s) of propagation of the source of the acoustic pressures. Also, instead of a pipe, any conduit or duct for carrying a fluid may be used if desired.

Also, the signals on the lines 20,22,24 (FIG. 1) may be time signals H₁(t),H₂(t),H₃(t), where Hn(t) has the pressure signal Pn(t) as a component thereof, such that FFT[H₁(t)]=G(ω)P₁(ω), FFT[H₂(t)]=G(ω)P₂(ω), and the ratio H₂(ω)/H₁(ω)−G(ω)P₂(ω)/G(ω)P₁(ω)−P₂(ω)/P₁(ω), where G(ω) is a parameter which is inherent to each pressure signal and may vary with temperature, pressure, or time, such as calibration characteristics, e.g., drift, linearity, etc.

Also, Instead of calculating the ratios P₁₂ and P₁₃, equations similar to Eqs. 9,10 may be derived by obtaining the ratios of any other two pairs of pressures, provided the system of equations Eq.5-7 are solved for B/A or A/B and the ratio of two pairs of pressures. Also, the equations shown herein may be manipulated differently to achieve the same result as that described herein.

Still further, if, for a given application, the relationship between A and B (i.e., the relationship between the right and left travelling waves, or the reflection coefficient R) is known, or the value of A or B is known, or the value of A or B is zero, only two of the equations 5-7 are needed to determine the speed of sound. In that case, the speed of sound a_(mix) can be measured using only two axially-spaced acoustic pressure sensors along the pipe.

Further, while the invention has been described as using a frequency domain approach, a time domain approach may be used instead. In particular, the Eqs. 5,6,7 may be written in the form of Eq. 1 in the time-domain giving time domain equations P₁(x₁,t), P₂(x₂,t),P₃(x₃,t), and solved for the speed of sound a_(mix) and eliminating the coefficients A,B using known time domain analytical and signal processing techniques (e.g., convolution).

Referring to FIGS. 37-40, it should be understood that although the invention has been described hereinbefore as using the one dimensional acoustic wave equation evaluated at a series of different axial locations to determine the speed of sound, any known technique to determine the speed at which sound propagates along a spatial array of acoustic pressure measurements where the direction of the source(s) is (are) known may be used to determine the speed of sound in the mixture. The term acoustic signals as used herein, as is known, refers to substantially stochastic, time stationary signals, which have average (or RMS) statistical properties that do not significantly vary over a predetermined period of time (i.e., non-transient ac signals).

For example, the procedure for determining the one dimensional speed of sound a_(mix) within a fluid contained in a pipe using an array of unsteady pressure measurements is similar to a problem encountered in underwater acoustics (e.g., SONAR or Sound Navigation Ranging). In underwater acoustics, axial arrays of sensors are deployed to determine the bearing (or direction) of underwater noise sources. The process is referred to as “beam forming”. In free space, i.e., in an unbounded media, such as the ocean, the speed at which a sound wave propagates along an axial array is dependent on both (1) the free-space speed of sound and (2) the incident angle of the sound wave on the axial array.

Referring to FIG. 37, the apparent sound speed a_(x) at which the wave propagates along the array is related to the angle or bearing (θ=90−γ) of the source S1 and the sound speed α in the media. For a SONAR application, as is known, the speed of sound is known and the apparent sound speed α_(x) is measured, which allows the bearing to be determined by the relation: θ=cos⁻¹(α/α_(x)).

Conversely, referring to FIG. 38, we have found that in a pipe 12 where the angle or bearing on the array of the incident sound is known, i.e., θ=0 deg, the speed of sound α of the fluid in the pipe 12 can be determined as follows.

In particular, referring to FIG. 39, for a single distant source in two dimensional (2D) space, the pressure wave can be written as follows (such as is generally described in A. Dowling and J. Williams, “Sound and Sources of Sound”, Ch 4, pp 79-81):

P(x,y,t)=Ae ^(iω(t−x sin γ) ^(₁) ^(/α−γ cos γ) ^(₁) ^(/α))  Eq. 27

Pressure as seen on the array at y=0 is:

P(x,y=0,t)=Ae ^(iω(t−x sin γ) ^(₁) ^(/α))  Eq. 28

$\begin{matrix} {{{P\left( {x,t} \right)} = {A\quad ^{{- }\quad k_{xr}x}^{\quad \omega \quad t}}}{{{where}\text{:}\quad k_{xr}} = {\left( {\sin \quad \gamma_{1}} \right){\frac{\omega}{a} \cdot}}}} & {{Eq}.\quad 29} \end{matrix}$

A similar analysis may be done for a left travelling wave along the array from the source S2 as: $\begin{matrix} {{{P\left( {x,t} \right)} = {B\quad ^{{+ }\quad k_{xl}x}^{\quad {\omega t}}}}{{{where}\text{:}\quad k_{xl}} = {\left( {\sin \quad \gamma_{2}} \right){\frac{\omega}{a}.}}}} & {{Eq}.\quad 30} \end{matrix}$

For the situation where the sound is propagating along a pipe, then γ₁=γ₂=90 deg. and where a=amix which is the speed of sound of the fluid mixture in the pipe, then: $\begin{matrix} {\quad {k_{xr} = \quad {k_{xl} = \frac{\omega}{a_{mix}}}}} & {{Eq}.\quad 31} \end{matrix}$

Thus, referring to FIG. 38, for a left and right travelling acoustic waves travelling in the pipe 12, the pressure equation becomes:

P(x,t)=Ae ^(−ik) ^(_(xr)) ^(x) e ^(iωt) +Be ^(+ik) ^(_(xl)) ^(x) e ^(iωt)  Eq. 32

which is the same as Eq. 1, and which may be used to determine the speed of sound by using the sensors described herein and solving the associated equations Eq. 5-7 shown hereinbefore. The same result may also be shown from sources originating in three dimensional space using cylindrical or other coordinate systems.

The data from the array of sensors may be processed in any domain, including the frequency/spatial domain (such as Eq. 4), the temporal/spatial domain (such as Eq. 1), the temporal/wave-number domain or the wave-number/frequency (k−ω) domain. As such, any known array processing technique in any of these or other related domains may be used if desired.

For example, Eq. 5 can be represented in the k−ω domain by taking the spatial Fourier transform of Eq. 5, resulting in the following k−ω representation: $\begin{matrix} {{P\left( {k,\omega} \right)} = {{\frac{1}{2\pi}{\int_{- \infty}^{+ \infty}{{P\left( {x,\omega} \right)}^{\quad {kx}}\quad {x}}}} = {{{A(\omega)}{\delta \left( {k - \frac{\omega}{a}} \right)}} + {{B(\omega)}{\delta \left( {k + \frac{\omega}{a}} \right)}}}}} & {{Eq}.\quad 33} \end{matrix}$

where k is the wave number and δ is the Dirac delta function, which shows a spatial/temporal mapping of the acoustic field in the k−ω plane.

Alternatively, instead of using the three equations Eq. 5-7, any technique known in the art for using a spatial (or phased) array of sensors to determine the direction of an acoustic source in three dimensional sound field with a known speed of sound (e.g., spatial array processing for SONAR arrays, RADAR (RAdio Detecting And Ranging) arrays or other arrays, beam forming, or other signal processing techniques), may be used to solve for the sound speed knowing the direction of travel of the acoustic waves, i.e., axially along the pipe. Some of such known techniques are described in the following references, which are incorporated herein by reference: H. Krim, M. Viberg, “Two Decades of Array Signal Processing Research—The Parametric Approach”, IEEE Signal Processing Magazine, pp 67-94, R. Nielson, “Sonar Signal Processing”, Ch. 2, pp 51-59.

Referring to FIG. 40, accordingly, the fluid parameter logic 60 may comprise spatial array processing logic 450 which receives the spatial array of acoustic pressure signals P₁(t), P₂(t), P₃(t) and performs the spatial array processing described herein to determine the speed of sound a_(mix) on the line 46.

By utilizing the output of sensor 10 of the present invention with various fluid properties related to speed of sound, such as density, a plethora of uses are enabled. For instance, signal processing logic 60 may contain simple look-up tables that include values of various parameters of fluids dependant on sound speed, such as the fluid type. Once the fluid density is determined the fluid type may be ascertained and reported by signal processing logic 60. Other examples of the use of the flowmeter of the present invention include determining the heating value of a fluid, the acid strength of sulfuric acid solution (or other acid or caustic mixture), the steam quality of a fluid, the salinity of fluid mixture, determining the phrase fraction for a three phase mixture and other known or contemplated uses where the sound speed and density of the fluid mixture yield powerful insight in determining other fluid values and compositions.

It should be understood that any of the features, characteristics, alternatives or modifications described regarding a particular embodiment herein may also be applied, used, or incorporated with any other embodiment described herein.

Although the invention has been described and illustrated with respect to exemplary embodiments thereof, the foregoing and various other additions and omissions may be made therein and thereto without departing from the spirit and scope of the present invention. 

What is claimed is:
 1. An industrial process control system for controlling at least one process parameter of an industrial process, said system comprising: an apparatus for determining at least one mixture parameter of a mixture flowing within a pipe of the industrial process, said apparatus comprising: a spatial array of at least two pressure sensors, disposed at different axial locations along said pipe, each of the at least two pressure sensors measuring an acoustic pressure within said pipe at a corresponding axial location, each of said pressure sensors providing an acoustic pressure signal at each of said corresponding axial locations; and a signal processor, responsive to said pressure signals, which provides an output signal indicative of the at least one mixture parameter related to a speed of sound of the mixture in the pipe; and a control device receiving said output signal and capable of controlling the at least one process parameter to a predetermined level.
 2. The control system of claim 1 wherein said signal processor comprises logic which calculates a speed at which sound propagates along said spatial array.
 3. The control system of claim 2 wherein said acoustic pressure signals each comprise a frequency based signal and wherein said signal processor comprises logic which calculates a ratio of two of said frequency based signals.
 4. The control system of claim 1 wherein said signal processor comprises logic which calculates a frequency based signal for each of said acoustic pressure signals.
 5. The control system of claim 1 comprising at least three of said sensors.
 6. The control system of claim 1 comprising three of said sensors and wherein said signal processor comprises logic which simultaneously solves the following equations for said speed of sound: P(x ₁ ,t)=(Ae ^(−ik) ^(_(r)) ^(x) ^(₁) +Be ^(+ik) ^(_(l)) ^(x) ^(₁) )e ^(iωt) P(x ₂ ,t)=(Ae ^(−ik) ^(_(r)) ^(x) ^(₂) +Be ^(+ik) ^(_(l)) ^(x) ^(₂) )e ^(iωt) P(x ³ ,t)=(Ae ^(−ik) ^(_(r)) ^(x) ^(₃) +Be ^(+ik) ^(_(l)) ^(x) ^(₃) )e ^(iωt) where A,B are amplitudes of the frequency based signals, x is the axial location of the pressure sensor along the pipe, t is time, ω is frequency, and k_(r),k_(l) are wave numbers.
 7. The control system of claim 1 wherein said signal processor calculates said speed of sound of said mixture using the following relation: ${\frac{^{\quad^{{- }\quad k_{r}x_{1}}} + {Re}^{\quad k_{l}x_{1}}}{^{\quad^{{- }\quad k_{r}x_{3}}} + {Re}^{\quad k_{l}x_{3}}} - \left\lbrack \frac{P_{1}(\omega)}{P_{3}(\omega)} \right\rbrack} = 0$ ${{{where}\quad R} \equiv \frac{B}{A}} = \frac{^{\quad^{{- }\quad k_{r}x_{1}}} - {\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{\quad^{{- }\quad k_{r}x_{2}}}}}{{\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{\quad^{\quad k_{l}x_{2}}}} - ^{\quad^{\quad k_{l}x_{1}}}}$ ${{where}\quad k_{r}} \equiv {\left( \frac{\omega}{a_{mix}} \right)\frac{1}{1 + M_{x}}\quad {and}\quad k_{l}} \equiv {\left( \frac{\omega}{a_{mix}} \right)\frac{1}{1 - M_{x}}}$

where a_(mix) is the speed of sound of the mixture in the pipe, ω is frequency (in rad/sec), and M_(x) is the axial Mach number of the flow of the mixture within the pipe, where: $M_{x} \equiv \frac{V_{mix}}{a_{mix}}$

and where Vmix is the axial velocity of the mixture, and where P₁(ω),P₂(ω),P₃(ω) are said frequency based signals for each of said acoustic pressure signals.
 8. The control system of claim 1 wherein said sensors are equally spaced, a Mach number of the mixture is small compared to one, and said signal processor calculates the speed of sound of the mixture using the following relation: $a_{mix} = \frac{\omega}{\left\lbrack \frac{1}{\Delta \quad x} \right\rbrack \quad {\log \left\lbrack \frac{P_{12} + {P_{13}P_{12}} + \left( {P_{12}^{2} + {2P_{13}P_{12}^{2}} + {P_{13}^{2}P_{12}^{2}} - {4P_{13}^{2}}} \right)^{1/2}}{2P_{13}} \right\rbrack}}$

where P₁₂=P₁(ω)/P₂(ω),P₁₃=P₁(ω)/P₃(ω), i is the square root of −1, Δx is the axial spacing between sensors, where a_(mix) is the speed of sound of the mixture in the pipe, ω is frequency (in rad/sec), and where P₁(ω),P₂(ω),P₃(ω) are said frequency based signals for each of said acoustic pressure signals.
 9. The control system of claim 1 wherein said sensors are equally axially spaced, a Mach number of the mixture is small compared to one, and said signal processor calculates the speed of sound of the mixture using the following relation: $\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = {2\quad {\cos \left( \frac{{\omega\Delta}\quad x}{a_{mix}} \right)}}$

where a_(mix) is the speed of sound of the mixture in the pipe, ω is frequency (in rad/sec), Δx is the axial spacing between said sensors, and where P₁(ω),P₂(ω),P₃(ω) are said frequency based signals for each of said acoustic pressure signals.
 10. The control system of claim 1 wherein the signal processor comprises logic which calculates a fluid composition of the mixture in the pipe.
 11. The control system of claim 1 wherein said signal processor comprises logic which calculates a fluid composition of the mixture using the following relation: $a_{mix} = \sqrt{\frac{1 + {\frac{\rho_{1}}{\rho_{2}}\frac{h_{2}}{h_{1}}}}{\frac{1}{a_{1}^{2}} + {\frac{\rho_{1}}{\rho_{2}}\frac{h_{2}}{h_{1}}\frac{1}{a_{2}^{2}}}}}$

where a₁,a₂ are known speeds of sound, ρ₁,ρ₂ are known densities, and h₁,h₂ are volume fractions of two respective fluids, and a_(mix) is the speed of sound of the mixture.
 12. The control system of claim 1 wherein said speed of sound is substantially determined by two fluids within the mixture.
 13. The control system of claim 1 wherein said pressure sensors are fiber optic pressure sensors.
 14. The control system of claim 1 wherein at least one of said pressure sensors measures a circumference-averaged pressure at said axial location of said sensor.
 15. The control system of claim 1 wherein at least one of said pressure sensors measures pressure at more than one point around a circumference of the pipe at said given axial location of said sensor.
 16. The control system of claim 1 wherein at least one of said pressure sensors measures strain on the pipe.
 17. The control system of claim 1, wherein the acoustic pressure signals are indicative of the background acoustic noise within the pipe.
 18. The control system of claim 1, wherein the control device includes at least one of a pump, valve and throttle.
 19. The control system of claim 1, wherein the at least one mixture parameter includes at least one of a fluid fraction, temperature, salinity, mineral content, mach number and speed of sound of the mixture.
 20. The control system of claim 1, wherein the mixture includes at least one fluid.
 21. A method for controlling at least one process parameter of an industrial process, said method comprising: measuring acoustic pressures within a pipe at at least two predetermined axial measurement locations along the pipe of the industrial process, wherein a mixture flows within the pipe; determining an output signal indicative of at least one mixture parameter of the mixture related to a speed of sound of the mixture using said acoustic pressures measured at said axial measurement locations; and controlling said at least one process parameter to a predetermined level in response to output signal.
 22. The method of claim 21 wherein said calculating step comprises calculating a speed at which sound propagates along said axial measurement locations.
 23. The method of claim 21 wherein said calculating step comprises calculating frequency based signals for said acoustic pressures.
 24. The method of claim 21 wherein said calculating step comprises calculating a ratio of two of said frequency based signals.
 25. The method of claim 21 wherein said measuring step comprises measuring acoustic pressure at at least three axial measurement locations along the pipe.
 26. The method of claim 21 wherein said measuring step comprises measuring acoustic pressure at three axial measurement locations along the pipe and wherein said calculating step comprises simultaneously solving the following equations for the speed of sound: P(x ₁ ,t)=(Ae ^(−ik) ^(_(r)) ^(x) ^(₁) +Be ^(+ik) ^(_(l)) ^(x) ^(₁) )e ^(iωt) P(x ₂ ,t)=(Ae ^(−ik) ^(_(r)) ^(x) ^(₂) +Be ^(+ik) ^(_(l)) ^(x) ^(₂) )e ^(iωt) P(x ₃ ,t)=(Ae ^(−ik) ^(_(r)) ^(x) ^(₃) +Be ^(+ik) ^(_(l)) ^(x) ^(₃) )e ^(iωt) where A,B are amplitudes of the frequency based signals, x is the axial location of the pressure sensor along the, t is time, ω is frequency, and k_(r),k_(l) are wave numbers.
 27. The method of claim 21 wherein said calculating step calculates said speed of sound of the mixture using the following relation: ${\frac{^{\quad^{{- }\quad k_{r}x_{1}}} + {Re}^{\quad k_{l}x_{1}}}{^{\quad^{{- }\quad k_{r}x_{3}}} + {Re}^{\quad k_{l}x_{3}}} - \left\lbrack \frac{P_{1}(\omega)}{P_{3}(\omega)} \right\rbrack} = 0$ ${{{where}\quad R} \equiv \frac{B}{A}} = \frac{^{\quad^{{- }\quad k_{r}x_{1}}} - {\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{\quad^{{- }\quad k_{r}x_{2}}}}}{{\left\lbrack \frac{P_{1}(\omega)}{P_{2}(\omega)} \right\rbrack ^{\quad^{\quad k_{l}x_{2}}}} - ^{\quad^{\quad k_{l}x_{1}}}}$ ${{where}\quad k_{r}} \equiv {\left( \frac{\omega}{a_{mix}} \right)\frac{1}{1 + M_{x}}\quad {and}\quad k_{l}} \equiv {\left( \frac{\omega}{a_{mix}} \right)\frac{1}{1 - M_{x}}}$

where a_(mix) is the speed of sound of the mixture in the pipe, ω is frequency (in rad/sec), and M_(x) is the axial Mach number of the flow of the mixture within the pipe, where: $M_{x} \equiv \frac{V_{mix}}{a_{mix}}$

and where Vmix is the axial velocity of the mixture, and where P₁(ω),P₂(ω),P₃(ω) are said frequency based signals for each of said acoustic pressures.
 28. The method of claim 21 wherein said measurement locations are equally axially spaced, a Mach number of the mixture is small, and said calculating step calculates the speed of sound of the mixture using the following relation: $a_{mix} = \frac{\omega}{\left\lbrack \frac{1}{\Delta \quad x} \right\rbrack {{log}\left\lbrack \frac{\begin{matrix} {P_{12} + {P_{13}P_{12}} +} \\ \left( {P_{12}^{2} + {2P_{13}P_{12}^{2}} + {P_{13}^{2}P_{12}^{2}} - {4P_{13}^{2}}} \right)^{1/2} \end{matrix}}{2P_{13}} \right\rbrack}}$

where P₁₂=P₁(ω)/P₂(ω), P₁₃=P₁(ω)/P₃(ω), i is the square root of −1, Δx is the axial spacing between sensors, where a_(mix) is the speed of sound of the mixture in the pipe, ω is frequency (in rad/sec), and where P₁(ω),P₂(ω),P₃(ω) are said frequency based signals for each of said acoustic pressures.
 29. The method of claim 21 wherein said measurement locations are equally axially spaced, a Mach number of the mixture is small compared to one, and said calculating step calculates the speed of sound of the mixture using the following relation: $\frac{{P_{1}(\omega)} + {P_{3}(\omega)}}{P_{2}(\omega)} = {2{\cos \left( \frac{{\omega\Delta}\quad x}{a_{mix}} \right)}}$

where a_(mix) is the speed of sound of the mixture in the pipe, ω is frequency (in rad/sec), Δx is the axial spacing between said measurement locations, and where P₁(ω),P₂(ω),P₃(ω) are said frequency based signals for each of said acoustic pressures.
 30. The method of claim 21 further comprising calculating a fluid composition of the mixture in the pipe.
 31. The method of claim 21 further comprising calculating a fluid composition of the mixture using the following relation: $a_{mix} = \sqrt{\frac{1 + {\frac{\rho_{1}}{\rho_{2}}\frac{h_{2}}{h_{1}}}}{\frac{1}{a_{1}^{2}} + {\frac{\rho_{1}}{\rho_{2}}\frac{h_{2}}{h_{1}}\frac{1}{a_{2}^{2}}}}}$

where a₁,a₂ are known speeds of sound, ρ₁,ρ₂ are known densities, and h₁,h₂ are volume fractions of the two respective fluids, a_(mix) is the speed of sound of the mixture.
 32. The method of claim 21 wherein the speed of sound is substantially determined by two fluids within the mixture.
 33. The method of claim 32 wherein said two fluids are: oil/water, oil/gas, or water/gas.
 34. The method of claim 21 wherein said measuring step is performed by fiber optic pressure sensors.
 35. The method of claim 21 wherein said measuring step is performed by fiber optic Bragg grating-based pressure sensors.
 36. The method of claim 21 wherein said measuring step measures a circumference-averaged pressure at said axial location of said sensor.
 37. The method of claim 21 wherein said measuring step measures pressure at more than one point around a circumference of the pipe at said axial location of said sensor.
 38. The method of claim 21, wherein the acoustic pressures measured are indicative of the background acoustic noise within the pipe.
 39. The method of claim 21, wherein the controlling step includes controlling at least one of a pump, valve and throttle to control said process parameter.
 40. The control system of claim 21, wherein the at least one mixture parameter includes at least one of a fluid fraction, temperature, salinity, mineral content, mach number and speed of sound of the mixture.
 41. The method of claim 21, wherein the mixture includes at least one fluid. 